WO2019143520A1 - Ensemble piston à tête flottante - Google Patents

Ensemble piston à tête flottante Download PDF

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Publication number
WO2019143520A1
WO2019143520A1 PCT/US2019/013050 US2019013050W WO2019143520A1 WO 2019143520 A1 WO2019143520 A1 WO 2019143520A1 US 2019013050 W US2019013050 W US 2019013050W WO 2019143520 A1 WO2019143520 A1 WO 2019143520A1
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WO
WIPO (PCT)
Prior art keywords
piston
chamber
floating
fluid
head
Prior art date
Application number
PCT/US2019/013050
Other languages
English (en)
Inventor
Joshua M. SCHMITT
Original Assignee
Thermal Tech Holdings
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thermal Tech Holdings filed Critical Thermal Tech Holdings
Priority to CN201980019056.2A priority Critical patent/CN111868368A/zh
Priority to JP2020540445A priority patent/JP2021520462A/ja
Priority to EP19741026.9A priority patent/EP3740665A4/fr
Priority to US16/963,080 priority patent/US11333101B2/en
Priority to CA3088731A priority patent/CA3088731A1/fr
Priority to KR1020207023646A priority patent/KR20200106949A/ko
Priority to RU2020127183A priority patent/RU2020127183A/ru
Publication of WO2019143520A1 publication Critical patent/WO2019143520A1/fr
Priority to PH12020551081A priority patent/PH12020551081A1/en
Priority to IL276104A priority patent/IL276104A/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/001—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type in which the movement in the two directions is obtained by one double acting piston motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/36—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide

Definitions

  • ORC equipment or engine manufacturers often provide a system that allows for practical operation with input heat temperatures as low as l70°F.
  • input heat temperatures as low as l70°F.
  • this may only be rendered where a dramatically reduced output is also attained, thereby making the undertaking significantly less economical.
  • this is due to the fact that the method of operation uses two phase changes per cycle, from liquid to gas and back again, and uses turbine or turbine-like technology to convert the pneumatic forces of the gas to generate productive work.
  • Such engines operate at a“low” rotational speed of near 5,000 rpm.
  • the gas mixture is then cooled back to a liquid state, changing phase again before reuse.
  • Even setting aside these naturally occurring phase change inefficiencies, such speed and phase changes create significant noise, not unlike a jet engine.
  • thermo hydraulic heat engines Another technology that has been attempted is known as“thermal hydraulic heat engines”. These involve the use of heat applied to a liquid that may have a relatively high coefficient of expansion. As a practical matter, however, most liquids expand very little when heated and contract very little when cooled. Thus, in actual practice, such engines fail to attain successful commercialization due primarily to the difficulty of obtaining sufficient expansion, and sufficiently rapid expansion and contraction, in liquids, which in turn limits the economic viability of such engines. Further, even when utilized, such engines are only practical for use in a narrow set of specific circumstances given the general inflexibility in terms of available modifications for differing uses. In fact, extensive trial and error is generally required even for the circumstances in which the engines may be effectively utilized. This is due, in part, to the inherent limitation involved with relying on the expansion and contraction of a liquid by the introduction and removal of heat.
  • a piston assembly for a thermal cycle engine.
  • the assembly includes a piston with a head defining an operating chamber for changing in volume.
  • a floating head is also included which defines a compressible chamber and is in hydraulic communication with the operating chamber to enhance reciprocation of the piston. Additionally, the compressible chamber volume is dynamically dependent upon the operating chamber volume.
  • the operating chamber is defined by the piston head at one side whereas the floating head itself defines the other side of the chamber.
  • the operating chamber is actually a first operating chamber and the hydraulic communication with the floating head includes a tubular connection from the first operating chamber to a second operating chamber defined by the floating head at a location apart from the first operating chamber.
  • Fig. 1 is a side perspective view of a unitary embodiment of a floating head piston assembly.
  • Fig. 2A is a schematic representation of a segmented embodiment of a floating head piston assembly.
  • Fig. 2B is an enlarged view of a portion of the schematic representation of the segmented embodiment of Fig. 2 A.
  • FIG. 3 is a schematic representation of a system employing a circulating operating fluid to direct reciprocation of the floating head piston assembly of Fig. 1.
  • Fig. 4A is a schematic representation of the system of Fig. 3 employing a circulating working fluid with a piston of the assembly in a first upper position.
  • Fig. 4B is a schematic representation of the system of Fig. 4A as the volume of an upper intermediate chamber is decreased by the piston to circulate working fluid therefrom.
  • Fig. 4C is a schematic representation of the system of Fig. 4B with the piston substantially closing the working chamber.
  • Fig. 4D is a schematic representation of the system of Fig. 4C with a lower floating head moving upward to facilitate the piston in decreasing a volume of a lower working chamber to circulate working fluid therefrom.
  • FIG. 5 is a flow-chart summarizing an embodiment of employing a floating head piston assembly in a system to produce work for supplying energy.
  • Embodiments detailed herein may use the controlled expansion and contraction of a compressible fluid, perhaps supercritical fluid, to move a piston in order to generate productive work. While it is not required that the operating fluid be a supercritical fluid, the system may govern a thermodynamic cycle similar to embodiments detailed in US Provisional Patent Application 62/424,494 for a Thermal Cycle Engine and PCT/US17/60722 for a High Dynamic Density Range Thermal Cycle Engine, each of which is incorporated herein in its entirety. For example, the engine may display a“low” reciprocation speed of less than about 50 cycles per minute. Further, embodiments detailed herein may avoid changes in phase, and so are inherently more thermodynamically efficient, and with the appropriate operating fluid may operate effectively using input temperatures below 200°F. In fact, they can easily be tuned to operate with minor reductions in efficiency with input heat below l50°F. It also operates with greatly reduced noise.
  • a unique floating head may be employed adjacent to a piston head to provide a sequentially timed, spring-like aid to filling the working fluid chamber and stroking of a piston for enhanced efficiency thereof.
  • a side perspective view of a unitary embodiment of a floating head piston assembly 100 is shown.
  • a working piston 110 shares the same monolithic housing 101 with floating pistons 142, 147.
  • the housing 101 may be of single construction or separately joined segmented pieces. For example, separate casings, one for each floating head 142, 147 and another for the working piston 110 may be separately constructed and welded together.
  • a unitary character is displayed by the monolithic housing 101 without the requirement of any hydraulic lines to support fluid communication between the working piston 110 and the floating pistons 142, 147.
  • a non-unitary, hydraulic line supported communications may be employed for sake of design flexibility (e.g. depending on available foot-space) (see Figs. 2A and 2B).
  • the assembly 100 is constructed such that reciprocation of the working piston 110 is used to alternatingly change the volumes of intermediate chambers 125, 126.
  • an incompressible working fluid such as hydraulic oil may be alternatingly circulated out of the chambers 125, 126 through working hydraulics 400 and directed toward a motor 430, flywheel 440, generator 450 or other suitable power retrieval device (e.g. see Figs. 4A and 4B).
  • the piston 110 Reciprocation of the piston 110 as described above is driven by the alternating introduction of operating fluid into adjacent chambers 150, 155 defined by working piston heads 114, 118.
  • the operating fluid may be a supercritical fluid such as C0 2 or other appropriate fluid, generally one that is effectively circulated by way of efficient heating and cooling cycles.
  • the volume of the upper intermediate chamber 125 is reduced, forcing working fluid out of the intermediate chamber 125 as noted above and toward a power retrieval device.
  • the piston 110 is reciprocated in the opposite direction, due to influx of operating fluid into the lower adjacent chamber 155, the volume of the lower intermediate chamber is compressibly reduced, again forcing working fluid out and toward a power retrieval device.
  • the floating chambers 140, 145 may be alternatively increased in volume, for example, by introduction of hydraulic oil or other suitable incompressible fluid from a nearby accumulator or other suitable location.
  • a chamber 140 may be increased in volume with the head 142 forced along the distance (d) toward the upper adjacent chamber 150 to aid in smooth controlled stroking of the piston 110 (to the right as shown).
  • working fluid may be circulated out of the upper intermediate chamber 125 as described above. Aid to circulating of the operating fluid out of the upper adjacent chamber 150 is also provided as a result of the movement of the floating head 142 in this manner.
  • This embodiment of floating head actuation and circulation of operating and working fluids is detailed further below with specific reference to Figs. 3 and 4A-4D, respectively.
  • the movement of the floating heads 142, 147 may be a function of pressure where the floating head chambers 140, 145 are sealed off and isolated without hydraulic connection to any outside pressure source.
  • a chamber 140 may be filled with a compressible gas such as nitrogen, air or an inert gas of a predetermined pressure sufficient for holding the head 142 at the head stop 175, say about 1,500 psi.
  • this feature may be referred to as a“gas” or an“air” spring as noted below.
  • the corresponding floating head chamber 140 may decrease in volume and increase in pressure.
  • this chamber 140 matches and/or exceeds pressure in the adjacent chamber 150, for example, with both reaching about 3,000 psi, the head 142 will be driven back toward the adjacent chamber 150, increasing pressure therein to provide an added kick for redirecting of the piston 110 in the opposite direction.
  • these pressures are only meant to be illustrative as any suitable range of pressure options may be employed.
  • the operating fluid which acts upon the piston 110 to drive reciprocation thereof may be a non-supercritical fluid, or a supercritical operating fluid such as C0 2 , helium or perhaps supercritical steam or other suitably efficient temperature effective fluid. That is, the fluid may be circulated through states of high temperature and pressure to states of low temperature and pressure, ultimately producing work.
  • the addition of the described floating head concept provides an energy storage and recovery device, illustratively referred to as a“gas spring” or an“air spring”, to the system which enhances the efficiency of this circulation.
  • This accumulator is initially kept at a set pressurization as indicated with a resulting temperature.
  • this spring upon pressurization and subsequent depressurization of the adjacent chamber helps regulate supercritical fluid circulation as indicated.
  • this action will maintain roughly a constant temperature condition in the gas of the chamber 140, improving the efficiency of the work produced by the cycle.
  • FIG. 2A and 2B a schematic representation of a segmented embodiment of a floating head piston assembly 200 is shown.
  • the piston 110 is housed separately from the floating heads 142, 147. More specifically, the heads 142, 147 are housed at discrete head chambers 220, 260 apart from the remainder of the assembly 200. Hydraulic lines 240, 280 are used to provide fluid communication between the heads 142, 147 and the adjacent chambers 150, 155.
  • the floating heads 142, 147 are positioned at the side of the head chambers 220, 260 closest to the adjacent chambers 150, 155.
  • the segmented embodiment of the assembly 200 differs slightly from the more unitary embodiment of Fig. 1. That is, the effective volume of the adjacent chambers 150, 155 is increased by the volume of the lines 240, 280 and by any exposed head chamber volume when a floating head 142, 147 shift to positions away from the adjacent chambers 150, 155. That said, the operating principles as detailed herein remain effectively the same.
  • the segmented embodiment of the assembly 200 of Figs. 2A and 2B may be found in terms of flexibility and options provided. For example, depending on where the assembly 200 is to be utilized at an industrial site, there may be foot-space limitations. However, the depicted embodiment allows for segmentation. Thus, the head chambers 220, 260 may be located in a separate location from the remainder of the assembly 200 with the hydraulic lines be extensive in length and flexibility if need be to provide the described hydraulic communications. As a practical matter, this may add to design flexibility and increase cost effectiveness for operations in an overall system.
  • FIG. 2A and 2B Another distinction for the embodiments of Figs. 2A and 2B may be found in the presence of the lines 260, 280.
  • the introduction of such tubular elements may present flow restrictions. In an embodiment where low rotational motor speeds are to be attained from the assembly 200 such restrictions may be negligible, particularly where an accumulator 490 is provided for pressure and volume regulation (e.g. see Fig. 4B).
  • the diameter of the lines 260, 280 may also be selected to minimize flow restriction.
  • the introduction of lines 260, 280 may be taken advantage of as a matter of providing additional design options.
  • FIG. 3 a schematic representation of a system 300 is shown employing a circulating operating fluid to direct reciprocation of the floating head piston assembly 100 of Fig. 1. That is, in this view, an embodiment of a hydraulic layout is shown for the operating fluid as it is employed to reciprocate the piston 110. This is in contrast to the corresponding hydraulic layout for the working fluid which ultimately supplies power, for example, as shown in the embodiments of Figs. 4A-4D.
  • floating heads 142, 147 are provided to facilitate enhanced reciprocation of the piston 110.
  • an operating fluid such as heated supercritical C0 2 has been routed from a heat exchanger 340 along line 330 which hydraulically links to heat side valves 335, 337.
  • the operating fluid may be altematingly routed to one of the upper 150 and lower 155 adjacent chambers of the piston assembly 100 to drive reciprocation thereof.
  • a heat flow 315 for example, heated water may be used to maintain heat of the heat exchanger 340.
  • maintaining the heat flow may be done by any of a number of low grade heat sources.
  • geothermal heat, solar heat or the waste heat from other unrelated system operations may be utilized to maintain the flow 315 at between about l00°F and 200°F. This allows for an effective and economical utilization of a vast array of heat sources previously considered to be too cool and of no practical economic value. Of course, in other embodiments, higher temperatures may be utilized.
  • the upper intermediate chamber 125 is about maximized in volume with the lower intermediate chamber 126 of Fig. 1 only negligibly apparent.
  • the working fluid has been forced out of the lower intermediate chamber and directed toward power retrieval device(s) as discussed further below.
  • the lower heat side valve 335 has been open directing operating fluid toward the lower operating chamber 155 while the upper heat side valve 337 has been closed.
  • the upper cold side valve 357 is opened with the lower cold side valve 355 remaining closed.
  • the upper floating head 142 may responsively begin to move upward as it slightly lags behind the upward movement of the piston 110 and upper head 114. Nevertheless, as noted above, this head 142 may also respond to a pressure buildup in the upper floating chamber 140, whether through pressurized air or the introduction of another working fluid, to initiate stroking of the piston 110 in the opposite direction following the depicted timeframe.
  • the upper cold side valve 357 will be closed as the lower 355 is opened to accommodate the flow of operating fluid therethrough.
  • the operating fluid is routed to a cold exchanger 360.
  • a recuperator 380 is first introduced into the flow of the operating fluid before reaching the cold exchanger 360.
  • the recuperator 380 may circulate operating fluid at an intermediate temperature, between that of the heat exchanger 315 and that of the cold exchanger 360.
  • a more consistent and efficient temperature drop may be displayed by the operating fluid before it reaches the cold exchanger 325.
  • the heat is recovered into the operating fluid after the pump 390, requiring less heat exchange from heat exchanger 340, thus improving cycle efficiency.
  • a cold flow 325 may be used to facilitate heat removal from the operating fluid by the cold exchanger 360. This flow 325 may be drawn from room temperature water, evaporative cooling or other suitable means.
  • the cooled operating fluid may then be pumped by an exchange pump 390 back through the recuperator 380 and eventually to the heat exchanger 340.
  • the circulating of the operating fluid to the piston assembly 100 for stroking of the piston 110 may be continued as described above.
  • FIGs. 4A-4D schematic representations of the system 300 of Fig. 3 are shown which highlight the hydraulics involved in the circulating of the working fluid as directed by the reciprocation of the piston 110 as described above.
  • the piston 110 of the assembly 100 is shown in a first upper position with the upper floating head 142 about to move upward (arrow 424).
  • this will pressurize or“charge” the upper floating chamber 140 which will subsequently provide an added force or kick for redirecting the piston 110 in the opposite downward direction.
  • an accumulator 490 is provided which may be used to direct a working fluid to this chamber 140 at the appropriate time to ensure a controlled sufficient added force is provided through a downward movement of the floating head 142.
  • the circulating of the operating fluid is used to continuously circulate working fluid from the assembly (arrow 400).
  • a working fluid may ultimately be directed to power retrieval devices as detailed further below (e.g. 430, 440, 450).
  • this fluid may also be directed toward power retrieval devices 430, 440, 450 as the floating head 142 is being set by movement upward (424) prior to being utilized as an aid in redirecting the piston 110 in the opposite direction.
  • a portion of this working fluid may be directed from the location of the power retrieval devices 430, 440, 450 to a reservoir 470.
  • a portion of the working fluid may be directed to the reservoir 470 making it available to the accumulator 490 for pressurizing upper floating chamber 140 as described above (or the lower floating chamber 145 (as described below).
  • an accumulator pump 480 is provided to help facilitate drawing on the reservoir 470 in charging the accumulator 490. Note, the upward movement of the accumulator piston 495 as the accumulator 490 is charged (arrow 497).
  • FIG. 4B a schematic representation of the system of Fig. 4A is shown as the circulation of hydraulic oil continues. Specifically, in this view, the volume of the upper floating head chamber 140 is decreased following the upward stroke of the piston 110 and the increase in pressure within the upper adjacent chamber 150. As described above, the pressure in the floating head chamber 140 will now be increased. In the embodiment shown, this increase is aided by the supplemental pressure provided by the accumulator 490. In this respect, the accumulator serves as a pressure and volume regulator of this chamber 140. In turn, this floating head 142 may be moved toward the piston 110 (arrow 423), increasing the pressure in the adjacent chamber 150 and forcibly directing the piston 110 back in the other direction (arrow 424). In this illustration, notice the movement of the accumulator piston 495 downward (arrow 498) to support the kick or“spring” effect of the upper floating piston 142 in the downward direction (arrow 423) as described above.
  • this working fluid may also be redirected to a reservoir 470 and made available to the accumulator 490 when not needed by the devices 430, 440, 450.
  • working fluid at the reservoir 470 that is not needed by the accumulator 490 may be recirculated right back to the assembly 100 at 410 with the aid of the accumulator pump 480.
  • FIG. 4C a schematic representation of the system 300 is shown with the piston 110 substantially closing the upper intermediate chamber 125 of Fig. 4B. This has been achieved with the aid of the upper floating head 142. It is apparent now that the lower floating head 147 may be shifted downward (arrow 404) in response to the corresponding increasing pressure of the lower adjacent chamber 155 as a result of the downward movement of the piston 110. As with the upward shift of the upper floating head 142, the downward shift of the lower floating head 147 may be employed to direct working fluid to the power retrieval devices 430, 440, 450 (e.g. along hydraulic line 405). Further, a portion of this working fluid may also be redirected from these devices 430, 440, 450 to the reservoir 470 as described above.
  • the power retrieval devices 430, 440, 450 e.g. along hydraulic line 405
  • the piston 110 may be ready for stroking upward again (see arrow 402). With the lower floating head 147 fully shifted downward and the pressure in the lower floating head chamber 145 at a maximum it is similarly ready to stroke upward to provide air spring like assistance to the upstroke of the piston 110. As with the upper floating head 142, this movement may be facilitated by the accumulator 490. Note the movement of the accumulator piston 495 in the downward direction 498 to provide this assistance.
  • FIG. 5 a flow-chart is shown which summarizes an embodiment of employing a floating head piston assembly in a system to produce work for supplying energy.
  • heated operating fluid is circulated to a piston in order to circulate working fluid from the location.
  • a floating head is also directed toward the piston to help facilitate these circulations.
  • working fluid is delivered to one of a variety of power retrieval devices as noted at 565 and thus, a functioning engine is provided.
  • the circulating operating fluid may then be allowed to cool 525 and eventually reheated 527 to continue the cycle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un ensemble doté d'un piston mis en mouvement alternatif à l'aide d'une tête flottante en communication fluidique avec le piston. L'ensemble peut employer une tête flottante dont la position est décalée pour favoriser le mouvement alternatif du piston avec l'aide d'une pression fournie à la tête flottante à partir d'un régulateur pression-volume. En variante, la tête flottante peut être en communication fluidique avec le piston d'un côté de la tête et isolée de l'autre côté. De cette manière, la modification du volume et de la pression sur ledit autre côté de la tête pendant le mouvement alternatif peut finalement conduire à un mouvement de la tête flottante vers le piston, favorisant ainsi la poursuite du mouvement alternatif. Des gains de rendement supplémentaires peuvent également être réalisés par l'intermédiaire de dispositions hydrauliques uniques pour les circulations de fluide de manœuvre et de travail.
PCT/US2019/013050 2018-01-18 2019-01-10 Ensemble piston à tête flottante WO2019143520A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
CN201980019056.2A CN111868368A (zh) 2018-01-18 2019-01-10 浮动头活塞组件
JP2020540445A JP2021520462A (ja) 2018-01-18 2019-01-10 浮動ヘッド・ピストン組立体
EP19741026.9A EP3740665A4 (fr) 2018-01-18 2019-01-10 Ensemble piston à tête flottante
US16/963,080 US11333101B2 (en) 2018-01-18 2019-01-10 Floating head piston assembly
CA3088731A CA3088731A1 (fr) 2018-01-18 2019-01-10 Ensemble piston a tete flottante
KR1020207023646A KR20200106949A (ko) 2018-01-18 2019-01-10 플로팅 헤드 피스톤 어셈블리
RU2020127183A RU2020127183A (ru) 2018-01-18 2019-01-10 Поршневой узел с плавающей головкой
PH12020551081A PH12020551081A1 (en) 2018-01-18 2020-07-15 Floating head piston assembly
IL276104A IL276104A (en) 2018-01-18 2020-07-16 Floating head piston assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862618689P 2018-01-18 2018-01-18
US62/618,689 2018-01-18

Publications (1)

Publication Number Publication Date
WO2019143520A1 true WO2019143520A1 (fr) 2019-07-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2019/013050 WO2019143520A1 (fr) 2018-01-18 2019-01-10 Ensemble piston à tête flottante

Country Status (10)

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US (1) US11333101B2 (fr)
EP (1) EP3740665A4 (fr)
JP (1) JP2021520462A (fr)
KR (1) KR20200106949A (fr)
CN (1) CN111868368A (fr)
CA (1) CA3088731A1 (fr)
IL (1) IL276104A (fr)
PH (1) PH12020551081A1 (fr)
RU (1) RU2020127183A (fr)
WO (1) WO2019143520A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022194877A1 (fr) * 2021-03-17 2022-09-22 Cixten Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5934076A (en) * 1992-12-01 1999-08-10 National Power Plc Heat engine and heat pump
EP1470014B1 (fr) * 2000-11-28 2006-04-19 Shep Limited Systemes de stockage d'energie hydraulique
US20090140475A1 (en) * 2002-05-29 2009-06-04 Turner Technology Group Hydraulic dampers with pressure regulated control valve
US20110041506A1 (en) 2008-01-23 2011-02-24 Barry Woods Johnston Adiabatic expansion heat engine and method of operating
US20120286522A1 (en) * 2009-06-29 2012-11-15 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
CN103195606B (zh) * 2012-04-01 2015-08-19 摩尔动力(北京)技术股份有限公司 做功单元热气机

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3100965A (en) * 1959-09-29 1963-08-20 Charles M Blackburn Hydraulic power supply
US3151533A (en) * 1961-08-01 1964-10-06 Cleveland Pneumatic Ind Inc Aircraft steering system
GB1033739A (en) * 1962-06-19 1966-06-22 Keelavite Hydraulics Ltd Hydraulically-operated reciprocating apparatus
US3901033A (en) * 1972-02-28 1975-08-26 Roy E Mcalister Vapor pressurized hydrostatic drive
US4044558A (en) * 1974-08-09 1977-08-30 New Process Industries, Inc. Thermal oscillator
US4195481A (en) * 1975-06-09 1980-04-01 Gregory Alvin L Power plant
US6470683B1 (en) * 1999-08-30 2002-10-29 Science Applications International Corporation Controlled direct drive engine system
GB2457476A (en) * 2008-02-13 2009-08-19 Nigel Alexander Buchanan Internal combustion engine with fluid, eg liquid, output
DE102012213878B4 (de) * 2012-08-06 2017-10-19 István Majoros Wärmekraftmaschine und thermodynamischer Kreisprozess zur Umwandlung von Wärme in Nutzarbeit
CN103047045B (zh) * 2012-12-18 2014-09-10 成都宇能通能源开发有限公司 一种蓄热式斯特林发动机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5934076A (en) * 1992-12-01 1999-08-10 National Power Plc Heat engine and heat pump
EP1470014B1 (fr) * 2000-11-28 2006-04-19 Shep Limited Systemes de stockage d'energie hydraulique
US20090140475A1 (en) * 2002-05-29 2009-06-04 Turner Technology Group Hydraulic dampers with pressure regulated control valve
US20110041506A1 (en) 2008-01-23 2011-02-24 Barry Woods Johnston Adiabatic expansion heat engine and method of operating
US20120286522A1 (en) * 2009-06-29 2012-11-15 Lightsail Energy, Inc. Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange
CN103195606B (zh) * 2012-04-01 2015-08-19 摩尔动力(北京)技术股份有限公司 做功单元热气机

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022194877A1 (fr) * 2021-03-17 2022-09-22 Cixten Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé
FR3120916A1 (fr) * 2021-03-17 2022-09-23 Pierre-Yves Berthelemy Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé

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US20200347799A1 (en) 2020-11-05
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US11333101B2 (en) 2022-05-17
EP3740665A1 (fr) 2020-11-25
CN111868368A (zh) 2020-10-30
KR20200106949A (ko) 2020-09-15
PH12020551081A1 (en) 2021-07-26
CA3088731A1 (fr) 2019-07-25
IL276104A (en) 2020-08-31
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